K- studley



Feb. 22, 1949. c. K. STUDLEY, .m

REVOLUTIONS COUNTER ACTUATOR 3 Sheets-Sheet 1 Filed June 3, 1946FJLE-E.B

INVENTOR CMRi/YCE K. 571/015 Y JR.

Feb. 22, 1949. c. K. STUDLEY, JR

REVOLUTIONS COUNTER ACTUATOR Filed June 3, 1946 5 heets-Sheet 2 INVENTORCum/m JTUDLEY JR.

Feb. 22, 1949.

Filed June 3, 1946 Anya/4r Rock 0/ N81) fi/ o/mr Order //1 Degrees c. K.STUDLEY, JR 2,462,690

REVOLUT IONS COUNTER ACTUATOR 3 Sheets-Sheet 3 Angular Rock 0/60/72r0////7 (7rd #7 Degrees F l E 5.;

INVENTOR; Cum/var If. STUULEY JR Patented Feb. 22, 1949 REVOLUTIUNSCOUNTER ACTUATGR Clarence K. Studley, din, Berkeley, Calif., assigncrMarchant Calculating Machine Company, a

corporation of California Application June 3, 1946, Serial No. 674,109

6 Claims. 1

The present invention relates to improvements in calculating machinesand has particular ref erence to counter actuating mechanisms for suchmachines.

The present improvements are disclosed as embodied in the commerciallyknown Merchant calculating machine described in the Avery ent Number2,271,240 dated January 27, 1942, to which reference is made for adisclosur or? the parts of the complete calculating machine which arenot specifically shown and described herein.

The counter in the calculating machine disclosed in the above mentionedpatent is of the crawl carry type which is operable at such higherspeeds than previously attainable, but this type of mechanismcontinuously transmits partial increments of movement from each or derto the next higher order during actuation of the numeral wheels, andconsequently certain of the numeral wheels are intermediate their fulldigital positions during a large part of the calculating operation. Thisdoes not ordinarily cause inconvenience, except in division calculationsduring which the operator cannot readily read the completed quotientdigits until the entire problem has been completed.

Counter mechanisms such as disclosed in the Chase Patent Number1,504,741 advance the numeral wheels intermittently by full digitalcrements and therefore the successive quotient digits can be read by theoperator during the process of division. The intermittent actuation iseiiected by actuator carry elements which are spring urged intooperative position when a carry should occur and are rocked out ofoperative position. against the spring pressure when a carry should notoccur.

If the prior art counter mechanisms of the type last mentioned wereoperated at a speed approximating that of the machine wlich the presentinvention is embodied, the springs would yield under the forces ofinertia and momentum and a carry would not always occur when. it should.On the other hand, the connections which are provided between thesuccessive elements to rock certain of these elements out of operativeposition, yield under the forces of momentum and the strength of theabove men-- tioned springs, and therefore cause a carry when the sameshould not occur.

In order to provide a counter which will record the registration in adirectly readable form in each order and which will at the time operateat speeds greatly in excess of those previouslyobtainable in such adirect reading counter, applicant devised a counting and tens-carry 1speeds and which is sufiiciently posi- Us action to safely hold theactuatorcarry elements out of operation except when a carry shouldoccur.

S ice the elements are thus held out by such .ve action, the strength ofthe springs which urge the elements into operative position can besuiiiciently to definitely insure movements of the elements intooperative position when a carry should occur.

It is the efore a primary object of the invention to rovide a high speedcounter which is capable of carrying the tens and registering the samein full digital increments during the calculation of a problem.

Another object of the invention is to prevent over-registration of acounter register of this class when oper ted at high speeds.

Another object of the invention is to positively prevent a tens carrywhen the same should not occur.

Another object of the invention is to increase the amount of movementfrom one tens carry element of a registering mechanism to another suchelement.

Another object of the invention is to transmit an increasing amount ofmovement from one element of a train of identical elements to suchelement.

Other objects and advantages of the invention will be apparent from thefollowing description of a preferred embodiment thereof, as illustratedin the accompanying drawings, in which: l is an enlarged plan view of aportion of -vention with the counting finger and carry e ments in fullcycle or normal position.

. 2 a similar view with the mechanism substantially mid-cycle positionshowing two of the carry elements in active positions for causing acarry to the next higher orders, while the other carry elements areshown in disenposition.

. is a sectional View from the right side dong line ill-J11 of Fig. 2.

. is sectional View from the right side a ong line IVIV of Fig. 2.

5 is a schematic View showing the relative movements of two adjacentcarry elements thnr connecting linkage.

5 is an enlarged right side elevation showing the counter actuatingmechanism in normal pos tion.

Fig. 7

schematically illustrates the path of movement of the point on thecounting finger or the carry element which engages the numeral wheeldrive gear.

Fig. 3 is a graph illustrating the amplification of the rocking movementtransmitted from each carry element to the next higher element.

Counter register The counter consists of an ordinal series of numeralwheels H8115 (Fig. 6 freely rotatable upon a stationary shaft i867.Secured to each wheel is a gear E8159 driven through an intermediategear Hill by a gear I880, freely rotatable on a shaft [92L the ratios ofthe gears I880 and lii'ii being such that for each tooth advancement ofgear i889 its associated numeral wheel is advanced from one numeral tothe next.

Centralizing of the numeral wheels is accomplished by means ofcentralizing pawl in (Fig. 6) freely pivoted on a shaft i8'i8 in eachorder. The rear arm Mi of each p-awl has a nose M2 which is urgedupwardly into contact with the teeth of gear i889 by a spring M lsecured to an arm I45 of the pawl and a frame stud Hi5. During rotation,the teeth of gear i385 will cam the nose M2 downwardly as each toothpasses above the nose, after which the pawl nose will seat itself in thenext tooth space, thus maintaining the proper alignment of gear I880 forthe next actuation by the counter finger or carry elements and alsoalignment of gears I819 to properly position the numeral wheels withrespect to the carriage cover openings.

Counter actuator One of the numeral wheels of the counter register isactuated through one digital increment during each machine cycle, tothereby register the multiplier and quotient digits in multiplicationand division operations and the items of addition and subtraction.

The actuation of the counter is efiected by a counter finger HI (Fig. 1)which is mounted on a bail Hill by means of a stud lZi. This bailincludes an arm llil formed on each end thereof and each of these armsis supported at its front end by a stud I 835 (Fig. 6) secured to themachine frame and disposed within a slot of the bail arm. The rear endof each arm is pivotally connected to a substantially vertical leverwith by means of a stud 02. The lower end of lever i830 is driven by aneccentric i83l mounted on a shaft i323 which is rotated one revolutionfor each machine cycle in either a clockwise or coun ter-clockwisedirection depending upon the setting of the reversing mechanism for plusor minus operation as disclosed in an Avery Patent Number 2,267,890dated December 30, 1941. A stud i832 mounted in the machine frame isdisposed within a camming slot [83211 which is so shaped as to coactwith the eccentric i83l' to produce a composite up and down and back andforth movement of the upper end of the lever and consequently a movementof the counter finger through a substantially triangular shaped pathshown in Fig. '7, so as to advance the gear i889 one tooth for eachcycle of the machine as described in the last mentioned Avery patent.

When the machine is set for plus operation the counter finger Iii (Fig.6) is dipped diagonally down and forwardly as indicated by the arrow inFig. 7 and moves underneath one of the teeth such as tooth W886i (Fig.6) of the gear I880 and engages same at point U (Fig. 7), and then movesupwardly along the path shown to advance the gear one tooth space. Thefinger then moves from beneath the gear tooth and becomes disengaged atpoint V after which it returns to the starting position at point S.During minus operation the counter finger moves in the oppositedirection along the same path and engages the top of one of the teeth ofthe gear and then moves downwardly and back to the position shown toactuate the gear i885 in th opposite direction.

In order to actuate one numeral wheel and then the next wheel asrequired in multi-order multiplication and division operations, a shifting mechanism is provided as disclosed in the Avery Patent 2,271,240referred to hercincefore. This shifting mechanism causes ordinalshifting movement of the carriage relative to the counter finger so asto permit actuation of the numeral wheel in one order and then the wheelin the next order in accordance with the process o multiplication anddivision.

The counter finger ill (Fig. l) is formed as a part of the lowest ordercarry element lZli and is rocked on stud 62! for reasons which will bedescribed hereinafter. The width of the finger however is such thatregardless of any rocking movement that may be imparted to the carrylever the finger ill will always be in engagement with its respectivegear ifiilii during every machine cycle.

Tens carry mechanism When a numeral wheel is driven by the abovedescribed counter actuator mechanism and passes from 9 to 0 in plusdirection or "0 to 9 in a negative direction, the tens digit is carriedto or subtracted from the next higher order to the left as viewed inFig. 1. Furthermore, if a series of adjacent numeral wheels display anun interrupted series of 9s and one of these is moved from 9 to 0 in aplus direction, all the higher order numeral wheels of the seriessimultaneously move from 9 to 0 and l is carried to the numeral wheel inthe order immediately to the left of the highest order numeral wheelwhich has thus passed from 9 to 0. This is known as simultaneous carryor chain carry, which will be described more fully hereinafter.

The tens carry mechanism includes a series of carry fingers or elementswhich are mounted on the same bail which carries the counter finger Hi.All the carry elements are capable of actuating the respective gearsrace with which they are aligned and operate at the same time finger ll!performs its actuation. These carry elements are spring urged intooperative position, but are held out and prevented from actuating exceptwhen the immediate lower order numeral wheel to the right in Figs. 1 and2 passes from 9 to 0 in a plus direction, or from 0 to 9 in a minusdirection. The construction of the carry elements and control thereof bythe next lower order numeral wheel is described below.

Carry Elements The carry elements I28 are in the form of bellcranks andeach is pivoted on a stud l2i secured to bail Hill. Each element isurged in a counterclockwise direction as viewed in Fig. 1 by means of aspring I22, one end of which is tensioned against a flange of the bailand the other end against a rivet 523 of the carry element. This rivetalso serves to positively limit the counterclockwise or What may betermed the forward movement of each element by engagement with the frontflange of the bail. Furthermore, the rivet I23 serves to secure toth'e'carry element a strap I24 which carries a roller i223. Extendingfrom the forward arm of each element E26 is a carry finger I26 normallypositioned opposite one of the gears E8393 and capable of engaging itduring actuation.

On the rearwardly extending arm of each element, except in the leftmostorder, is pivotally mounted by means of a stud I28, one end of a link436. A stud l3l, mounted on the other end of the link, is disposedwithin a slot I21 of the adjacenthigher order carry element I213. Thelinks ltd are alternately arranged on the top and bottom surfaces,respectively, of successive carry elements in order to avoid a collisionof parts during operation. The adjustment of the mechanism shown in rig.1 is such that when in the normal condition of rest, the rivet 123should rest against the front fiange of the bail and the stud [3i shouldbe positioned at the extreme inneriportion or upper right hand end ofslot I21. If' an adjustment is necessary to meet the foregoingrequirement, the length of the link 30 may be decreased by inserting ascrewdriver between the lugs of the one of the link and twist- ..Qg teairlg, or it may be increased by applying pressure with a pair of pliersagainst the outer edges of the-link across the opening.

Control from next lower order The mechanism that determines which of theabove described carry elements will be permitted to actuate theirrespective gears wild and numeral wheels for causing a tens carry fromone order to the next under the conditions described hereinbefore andwhich wi l be blocked out to prevent such a tens carry consists of adisc 82 splined or otherwise secured to a sleeve of the gear I880 in thenext lower order as clearly seen in cross section in Fig. 1. Each disc82 has a notch 83 in its periphery adapted to receive roller 125 of thecarry element during actuation when the numeral wheel which is geared torotate with said disc is positioned at 9 during plus operation or atduring minus operation.

The relationship between the zero and nine positions of the numeralwheels and the plus and minus operation of the carry element may beseenin'Fi'g; 6. Iii-this figure, the numeral wheel i815, by way ofexample, stands at zero and the notch 83 in disc 82 is above the fingerH I in the operating order and the other discs are in the same relationto the carry fingers I26 in those higher orders in which the numeralwheels stand at Zero. During minus operation the fingers all moveupwardly and toward the left as viewed in Fig. 6, and the roller E in agiven order will enter its respective notch and permit the finger toengage and drive its respective gear I889. If, however, the operationwere in a plus direction the fingers would move downwardly and to theleft and the roller would be blocked by the periphery of the disc toprevent movement of the finger into engagement with the gear.

When a given numeral wheel stands at nine, the notch in the disc isbelow the carry and/or counter finger, as the case may be, by the sameamount that it is shown above the finger in Fig. 6. The upward movementof the fingers during minus operation as described above will bring theroller against the "periphery of its disc and a tenscarry will beprevented; whereas during plus operation and th consequent downwardmovement. of therfingers with anumeral wheel stand- Cir ing at nine, theroller will enter its respective notch and permit its carry finger toengage and drive the gear 1880.

When a numeral wheel is positioned at any other number than zero ornine, the notch 83 of the will not be in either of the positionsdescribed above, the notch being shown in its #1 position in Fig. 3.When such is the case, the periphery of the disc will block the rollerduring actuation of the fingers in either direction and wiil rock thecarry element and finger lZS away rem gear @836 to prevent a carryentry.

The period of the cycle during which this blocking out occurs will bedescribed hereinafter, but it should be noted at this time that when thedisc a given order is in position to block the roller and carry finger,the carry elements move from the position shown in Figs. 1 and 6 to theposition shown '11 Figs. 2 3, the roller being blocked, contacts thedisc and rocks the carry i888 so that during the movement of the finger:etween points U and V (Fig. 7) it passes clear of the gear; whereas acarry element which is not blocked by its disc moves into engagementwith the gear in the next higher order as shown to the right of 2 andthus drives that gear one tooth and actuates the numeral wheel onedigital increme t dur ng the d ving phase of the cycle.

I L n con- .ple which a nurn al wheel stands at 9 during plus actuationbut during which no carry will be transmitted to the next higher order.This condition would exist in case three adjacent orders stand at 9 5 9,for example, and in 1 is added to the lowest order e standing at 9. Inthis instance a 1 Will carried to and added to the 5, advancing themiddle numeral wheel to 6, but the highest order numeral wheel standingat 9 will ct carry to the numeral wheel to the left The means forpermitting a carry from the lower order 9 and at the same time forpreventing a carry from the higher order 9 is as fol ows:

The two niiimeral wheels standing at nine have their notches in positionto permit movement of their carry fingers into actuating position and inthis case the lower order finger is permitted to perform such a carry tothe intermediate order. Since, however, this intermediate order standsat five, the periphery of the intermediate disc rocks the next and allother higher order carry elements out of operation, including the oneassociated with the higher order numeral wheel standing at nine, andtherefore prevents the carry from that order even though its associateddisc is located with its notch in position to permit a carry.

Simultaneous carry operation ed in co--nectf.on with a simple carryoperation for carrying the tens to th next higher nee-us carry through acontin- "al wheels occurs under conmh as a series of numeral wheels nineon... of the lower order wheels passes from nine to Zero in a plusdirection or if the series stands at zero and the lower order wheelpasses from zero to nine a minus direction: Taking the latter conditionas an example, then in accordance with the foregoing description, thenotches 83 in all orders in which the numeral wheels stand at zero arein the position shown in Fig.6. The carry finger 526 (Fig. 2) will bepermitted to move into operating position as shown and drive the gearI888 in the next higher order. Since the dial in this next order standsat zero the roller I25 will not be blocked and the counter finger willbe free to move into operating position and drive the third gear at thesame time the first and second gears are driven and so in each orderwhere the numeral wheels of a continuous series stand at zero. The firstnumeral wheel however which stands at other than zero will have its disc82 in a position such as that shown in Fig. 3 and this disc will blockthe carry element and prevent a carry into the next and all higher ordernumeral wheels.

It may be seen therefore that a carry will be entered into the numeralwheels displaying a continuous series or chain of zeros during minusoperation, but the carry will be interrupted by the first numeral wheelstanding at other than zero regardless of whether zeros stand in thenumeral wheels above that. A similar simultaneous chain carry will occurwhen the continuous series of numeral wheels stand at nine during plusoperation.

Mechanism for increasing the movement between carry elements As pointedout in the introduction and statement of the invention, prior art tenscarry mechanisms of this class sometimes fail to effect a carry when oneshould occur and sometimes cause a carry when the same should not occur,particularly at high-speed operation. This is caused by the higher ordercarry elements lagging behind the element which is positively held outby the disc in the controlling order, with the result that the carryelements in the higher orders of the L1 register are not held out ofactuating condition by sufficiently positive means; therefore, duringhigh-speed operation of such a machine, a higher order carry elementoccasionally engages the tip of a numeral wheel gear with sufiicientforce to the present improved mechanism is to operate at extremely highspeed. The linkages between the carry elements are therefore so arrangedand proportioned as to amplify or increase the disabling movement fromone carry element to the next, to thereby compensate for this wear andplay between the parts. Furthermore, the disabling movement of the carryelements is completed by the time those carry elements which arepermitted to efiect a carry, engage the gear teeth of their associatedgears.

Amplification of the disabling movement from one carry element to thenext can be provided in a number of different ways which would simplytransmit movement from one carry element to the next at any suitablefixed ratio. If the movement transmitted at such a fixed ratio weresufficiently great to insure complete disablement of the carry elementin the next higher order, then this would produce excessiveamplification when compounded through a series of orders. The mechanismdisclosed herein is therefore proportioned in such a way as to produce acontinuously diminishing amount of amplification throughout the rockingmovement of the carry elements, the movement being ample to cause singleorder disablement of the carry elements without excessive compoundedamplification of movement through a series of orders.

An understanding of the amount and timing or the amplifying movementfrom one order to the next can be most clearly attained by consideringthe diagrammatic representation in Fig. 5 of the mechanism shown inFig. 1. Points l2| and 52m (Fig. 5) represent the pivot points of twoadjacent carry elements lZB and correspond to the studs i2 5' (Fig. 1)upon which two adjacent carry elements are pivoted, and a (Fig. 5) isthe distance between these studs. Points I28 and 53! represent the studsof the same numbers in Fig. l, and b is a line drawn between points HIand !28 of the lower order, while 0 is a line between points i2|a andl3! of the higher order. Line 9353 drawn between points I28 and I3!represents the line of action of ,the link of the same number in Fig. 1,and is shown in the position in which it lies when the carry elementsare in their enabled positions, while I30 represents the line of actionof the same link when the carry elements are in their disabledpositions, shown at the left of Fig. 2. Lines m and n are normals frompoints [2! and 52m respectively to the line 53'} while lines m and n arenormals from the same respective points to the line I38. A is the anglesubtended by the normal n and line 0, and B is the angle subtended bythe normal m and line I), while angle D represents the angular rock ordisplacement of line 0 which is produced by the anguiar rock ordisplacement of line 19 through angle E which latter displacement isproduced by disablernent of the carry elements in the lower controllingorder by disc 82 as described hereinbefore.

Assuming for the purpose of the present discussion that lines b and care equal, then a difierence in the initial angles A and B will cause acorresponding difference in the displacement angles D and E;furthermore, when angle A is greater than angle B, the displacementangle D will exceed that of the given angle E. In other words, the givenmovement or displacement of line b through angle E will cause theresulting displacement of line 0 to be greater than that of line b. Thismay be termed amplified movement and the difierence between the greaterand the lesser displacements is the amplification. Moreover, the greaterthe difference between angles A and B, the greater will be theamplification. The amplification at any stage of the movements of linesI; and 0 through angles E and D respectively, is proportional to theratio m/n of the lengths of the normals which are the perpendiculardistances from line I36 to the points i2! and Mia respectively.

A further and more important characteristic of this organization is thatthe amount of angular displacement imparted to line 0 by any givenincrement of movement of line b will vary throughout such movement dueto the change in the line of action of link l3!) from the solid line A39to the dotted line 5353' (Fig. 5), and the amplification of movementfrom b through link or line I36 to c for producing the angulardisplacement of the latter will be greatest at the beginning of themovement and will decrease thereafter. Let us call this a change inamplification which in this case gives a greater initial.

amplification at the beginning of the cycle, and this may be calledearly amplification which is reduced to substantially zero finalamplification at the end of the disabling movement of the next higherorder carry element as the line ii becomes parallel to line a.

With this in mind let us consider oneoi the objectives of the invention.First, recall that the Counting finger H l and the carry elements i2 5(Figs. 1 and 6) move into a position to engage and drive the teeth ofthe respective gears i839 during approximately the first third of thecycle, and then actually start and effect the driving movement duringapproximately the second third of the cycle. If the higher order carryelements are to be blocked out of operation, this blocking out should bedone as early in the cycle as possible so none of the carry elementswill engage the tip of its gear or the corner of the notch 83 of thedisc 82 which might otherwise cause a misoperation, or even rub againstthe periphery of the disc during any part of the cycle which wouldotherwise cause the numeral wheel to flicker. It is therefore an objectto provide enough early amplification to rock the next higher carryelement and its roller clear of its respective disc safely before thedriving phase of the cycle starts, but at the same time to reduce theamplification in such a manner that the movement will be transmittedfrom order to order at a diminishing ratio. In other words, theamplification is reduced from an initial maximum to substantially zerowhen sufficient or optimum disabling movement is built up and thenbecomes a negative amplification thereafter so that the movement whichis compounded through a series of orders will not become excessive atthe high or left-most end of the series of elements.

If the lengths of lines b and were the same, and the difierence inangles A and B were great enough to give this required earlyamplification, then the total amplification through one order and thecompounded amplification through a series of orders would be in excessof the requirements of the mechanism shown. Therefore, in order tomaintain the desirable change in amplification, which will afiord therequired early amplification and at the same time reduce the totalamplification, the difference in angles A and B has been maintained andline 0 has been increased; i. e., the length of line c has been madegreater than line b by a sufiicient amount to give the over all or totalamplification required, while still maintaining the early amplificationdescribed above.

The change in amplification and the total amplification can becontrolled to satisfy any given requirements by proportioning the anglesA and B and selecting the lengths of line b and c in accordance with theforegoing and the following discussion. In the preferred embodiment ofthe invention shown, the components have been proportioned to amplifyapproximately 18.5 degrees of movement of line 13, designated angle E(Fig. to approximately 20.5 degrees of movement of line 0, designatedangle D, which is a total single order amplification at a ratio of1.109. Of this total amplification, the initial amplification is at theratio of 1.21 and the final amplification is at the ratio of 0.98 orslightly less than zero amplification in a single order.

A still more important and advantageous result is produced by theorganization described above. As pointed out briefly hereinbefore, ifsufficient amplification were provided to insure, disablement of thecarry element in the next higher order and if this amplification wereata fixed ratio, then the compounded amplification through ten orderswould produce a rocking movement in highest order which would be far inexcess of n optimum amount if not actually prohibitive iron-.1 thestandpoint of loads and shocks encountered in actual operation of themechanism at high speed. By way of example, suppose the op total singlerder amplification ratio were is in the embodiment disclosed. If this 2,ratio, then. the compounded amticn through ten orders would be in the oof (1.l@9) :2.52. This would increase the lgular rocking through aseries of ten carry eleats from 16.5 in the lowest order to 46.6'. inthe highest order which wou d be an increase of The action of themechanism disclosed herein which affords a diminishing ratio ofamplification and consequently a greatly reduced compoundedamplification is charted in Fig. 8. The horizontal components of the.points on the curves represent the angular roci: in degrees of the carryelement in a controlling ordenwhile the vertical components representthe angular rock in degrees of the carry element in the next higherorder. The line 290 is a 45 line which shows the angulardisplacement oftwo adjacent carry elements if the same were displaced at a i to 1 ratioand therefore constitutes a base line from which theadditional rock ofthe next higher order carry element may be measuredwhile curve 2 3irepresents the actual relationship between the angular rock of the carryelements as disclosed. The zero point on the graph represents theinitial position of lines 1) and c (Fig. 5). Point 1 on line 2% (Fig.

8) represents and rock of the controlling order and corresponds to the18.5 angle E (Fig. 5). Point Ea indicates the 20.5" angular rock. of thenext higher order carry element through angle D (Fig. 5) for the given18.5 rock of the lower order element. Line ib therefore represents theincrease in angular rocking movement from the lowest order carry elementto the next higher order element.

When no tens carry is effected during the operation of the mechanism,assuming that the lowest order is the controlling order and the elementin that order is blocked by its disc, then all the higher order carryelements are rocked simultaneously and the rocking, movement istransmitted from each carry element to the next higher element.Therefore, each element is, in effect, the controlling element for thenext higher element and causes an amplified rocking movement from one tothe other. This orderto-oroler amplification is illustrated by a seriesof steps composed of lines drawn horizontally and vertically between thepoints i, 2, 3, etc, and la, 2a, 311, etc., respectively on the curvesand Bill.

Now comparing the graph in Fig. 8 with the mechanism shown in Fig. i, itwill be noted that the 18.5 point i on the curve may econsidered torepresent the l8.5 rocking movement of the stud I28 about the pivot wtof the lowestorder carry element which drives the stud l3! of the nexthigher order carry element through 20.5", and the rock of this latterstud is represented by the 20.5 point to, (Fig. 8). Since stud I28 (Fig.l) of the next higher order or second carry element is mounted forrocking movement with that element, it too rocks through 20.5". Point 2therefore corresponds to the movement of the stud I28 in the secondorder element and this stud drives the stud I3| in the third carryelement through a total of approximately 225 as shown by the horizontalline from point 2a to the vertical scale of degrees. The steps betweenpoints 3 and 3a, 4 and 4a, etc. represent the rocking movements of therespective orders which will all go on simultaneously.

The change in the above described amplification of movement from onecarry element to the next may be seen by examining the curve 2M. It willbe noted that the ratio of the angular displacement between two adjacentcarry elements at any given stage of that displacement is proportionalto the slope of curve 213! at the corresponding point on the curve; andthis in turn is equal to the ratio of the length of the normal m to thatof the normal n at that stage of the operation. The slope at the initialzero point is indicated graphically by the line 202 which is tangent tothe curve at the zero point. The numerical value of the ratio at thisinitial zero point is therefore the value of the tangent of the anglesubtended by line 202 with the horizontal; i. e., tangent of 50 26=l.2l.

The fact that angle A (Fig. 5) exceeds angle B causes the normal n toincrease in length more rapidly than the normal m increases during theprogress of the movement, and to continue to increase after the lengthof the normal m is decreasing, thus causing a continuous decrease in theratio of amplification during the progress or" the movement. Thisdecrease in amplification is represented in Fig. 8 by the downwardcurvature of line 20!, the rate of such downward curvature beingcontrolled by the amount by which angle A exceeds angle B.

The slope of line 20! is greater than the slope of line 2053 at anypoint from zero up to the point la. This indicates that the differencein the amount of rock of two adjacent carry elements continues toincrease up to that stage of the rocking movement. The slope of line 2mdecreases, however, and at about the 18 point on line 2M, just belowpoint la, the slopes of the two lines are equal which indicates that atthis point the ratio of the movements is 1:1, and the difierence in theamount of rock becomes zero. From the foregoing it will appear that thepoint at which the slope of curve 2M becomes equal to the slope of line290 is determined jointly by the initial slope of curve 20] at the zeropoint in accordance with the length of the normals m and n at the startof the rocking movement, and by the rate of change of the slope of curve2m in accordance with the initial angles A and B.

It will be noted further that at the 18 point the above mentioneddifference changes sign from plus to minus and the ratio changes fromvalues greater than 1 to values less than 1. This may be seen by notingthat the curves 280 and 2M converge beyond point la and theperpendicular lines between points 2 and 2a to 9 and 9a inclusive becomeshorter and shorter. The diiierence in rock from each carry element tothe next therefore gradually changes from a maximum at about point lawhere it is needed to hold the next order carry element safely clear ofits disc and gear, and becomes less and less beyond this point, therebyreducing the total compounded amplification through ten orders. Thistotal compounded amplification is also determined jointly by the initialslope and rate of change of the slope of curve Zlll in accordance withthe initial lengths of the normals m and n and the initial angles A andB described above.

As stated hereinbefore, the carry elements are disabled prior to or atleast by the time the tens carry actuating phase starts. Fig. 7illustrates the various phases of the cycle and paths which the enabledand disabled carry fingers follow during these phases. The largesubstantially triangular path is that of the carry finger Ill and/or thefinger E28 (Fig. 1) of the carry element I28 when the latter is enabledto efiect a carry, and the dotted outline E8801; is that of the toothl88ila (Fig. 6) which is in position to be driven. The finger H l or lZtstarts from its full cycle position at point S and moves idly downwardlyand toward the left in the direction of the arrow during plus operationand then engages the tooth at point U which may be regarded as the startof the actuating phase. The finger then moves upwardly to point V thusdriving the gear i880 one tooth and then returns to the normal fullcycle position at S.

During minus operation, the finger travels in the opposite direction onsubstantially the same path and drives the gear in the oppositedirection. It will be noted that this path is not symmetrical about aline through the full cycle position S of the finger and the gear toothl88ila. This is because the openings for studs I832 and 5835 (Fig. 6)were drawn on simple arcs to simplify the tooling of this mechanism forproduction, but this path could as well be made symmetrical by makingthe openings more irregular to suit.

A finger which is to be disabled starts on the same path and at point T,the roller thereon engages the periphery of its associated disc 32 whichblocks further inward or leftward movement of the finger 526. As pointedout hereinbefore the roller H25 and disc 82 (Figs. 1 and 2) serve as afulcrum for the carry element [20 so that as the stud l2! movesdownwardly as viewed in these figures, the finger H5 in the disabledorder stops at point T and then backs away from the gear along the pathshown by line I88! (Fig. '7) and then moves idly upward to point Wduring the time the enabled fingers move through their actuating phaseto point V and through their disengaging phase to point W, all returningtogether to the position of rest S.

The carry fingers in the orders above or to the left of the one which isblocked by its disc 82 are also held out by the linkage describedhereinbefore and due to the amplification also described hereinbeiore,move along a path slightly to the right of line I88! thereby holding allthe rollers away from their discs 82. This completely avoids anypossibility of the higher order rollers striking the corners of thenotches 83 (Fig. 6) during the idle operation of the disabled carryelements. This avoids what is known as dial flicker and also avoidserroneous actuation of the drive train to the numeral wheel when themachine is operated at very high speeds.

I claim:

1. In a calculating machine having a revolution counter including aseries of ordinally arranged numeral wheels, each rotatable to positionsindicative of the digits zero to nine inclusive, and tens carrymechanism between said wheels including, a series of ordinally arrangedcarry elements each operable to actuate its respective numeral wheel andeach pivotally mounted for diiierential rocking movement of the same outof operative relationship with said numeral wheel, and means operable inaccordance with the position of the immediate lower order numeral wheelto cause said rocking movement; the combination of, means fortransmitting said rocking movement from one lower order carry element tothe next higher order carry element including a link pivotally connectedto said lower and higher order carry elements, the points of pivotalconnection of the link to the respective carry elements being so locatedwith respect to the point of pivotal mounting of the respective elementthat when the elements are in their normal condition of rest the anglesubtended by a normal drawn from the pivotal mounting of the higherorder carry element perpendicular to the line of action of said link anda radial line drawn from said pivotal mounting to the pivotal connectionof said element and said link is greater than the angle subtended by anormal drawn from the pivotal mounting of the lower order carry elementperpendicular to said line of action and a radial line drawn from thelatter pivotal mounting to the pivotal connection of the latter elementand said link.

2. The invention set forth in claim 1 in which the product of the lengthof the first mentioned radial line times the cosine of the firstmentioned angle is less than the product of the length of the lastmentioned radial line times the cosine of the last mentioned angle.

3. In a calculating machine having a revolution counter including aseries of ordinally arranged numeral wheels each rotatable to positionsindicative of the digits zero to nine inclusive and tens-carry mechanismbetween said wheels including, a series of ordinally arranged carryelements each operable to actuate its respective numeral wheel and eachpivotally mounted for differential rocking movement of the same out ofoperative relationship with said numeral wheel, and means operable inaccordance with the position of the immediate lower order numeral wheelto cause said rocking movement; in combination with, means fortransmitting said rocking movement from one lower order carry element tothe next higher order carry element including a link pivotally connectedto said lower and higher order carry elements, the points of pivotalconnection of the link to the respective carry elements being so locatedwith respect to the points of pivotal mounting of the respectiveelements that the perpendicular distance from the pivotal mounting ofthe lower order carry element to the line of action of the link isgreater than the perpendicular distance from the pivotal mounting of thehigher order carry element to said line of action.

4. The invention set forth in claim 3 wherein the ratio of the firstmentioned perpendicular distance to the second mentioned perpendiculardistance is greater during the initial rocking movement of said elementsthan it is during the later rocking movement of the same.

5. The invention set forth in claim 3 wherein the ratio of the firstmentioned perpendicular distance to the second mentioned perpendiculardistance is greater than one during the initial rocking movement of saidelements and diminished thereafter to a ratio substantially equal toone.

6. The invention set forth in claim 3 wherein the ratio of the firstmentioned perpendicular distance to the second mentioned perpendiculardistance is greater than one during the initial rocking movement of saidelements and diminished to a ratio substantially equal to one at thestage of an optimum rocking movement of said elements and to a ratioless than one thereafter.

CLARENCE K. STUDLEY, JR.

REFERENCES CITED UNITED STATES PATENTS Name Date Friden Oct. 30, 1945Number

